WO2018199490A1 - Moteur rotatif - Google Patents

Moteur rotatif Download PDF

Info

Publication number
WO2018199490A1
WO2018199490A1 PCT/KR2018/003886 KR2018003886W WO2018199490A1 WO 2018199490 A1 WO2018199490 A1 WO 2018199490A1 KR 2018003886 W KR2018003886 W KR 2018003886W WO 2018199490 A1 WO2018199490 A1 WO 2018199490A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
lobe
rotor
housing
rolling
Prior art date
Application number
PCT/KR2018/003886
Other languages
English (en)
Korean (ko)
Inventor
유병훈
이윤희
오휘성
이병철
Original Assignee
엘지전자 주식회사
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Priority to CN201880027416.9A priority Critical patent/CN110546360B/zh
Publication of WO2018199490A1 publication Critical patent/WO2018199490A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/02—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B55/00—Internal-combustion aspects of rotary pistons; Outer members for co-operation with rotary pistons
    • F02B55/08—Outer members for co-operation with rotary pistons; Casings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a rotary engine for producing power in a rotary motion.
  • Rotary engines are engines that produce power in rotational motion and were originally designed by Wankel.
  • the Wankel engine devised by Wankel includes a housing whose inner surface is formed of an epitrocoid curve and a triangular rotor rotating within the housing.
  • the inner space of the housing is divided into three spaces by the rotor, and the volume of these spaces is changed in accordance with the rotation of the rotor, so that four strokes of intake ⁇ compression ⁇ explosion ⁇ exhaust occur continuously.
  • each stroke is performed three times while the rotor is rotating, and the eccentric shaft is configured to be three revolutions.
  • Wankel engine Since the development of the Wankel engine, various researches have been conducted to optimize the design of the Wankel engine, and a modified rotary engine has also been developed.
  • the rotary engine is easy to miniaturize due to its simple structure and is a high power engine capable of producing high power in high speed operation. Due to these features, rotary engines have the advantage of being applicable to various devices such as heat pump systems, automobiles, bicycles, aircraft, jet skis, chain saws and drones. In addition, the rotary engine has the advantage that the rotational force is uniform, less vibration and noise, and less NOx emissions.
  • the rotary engine has a large surface area compared to the stroke volume, the anti-inflammatory area is enlarged, and a large amount of unburned hydrocarbon (UHC) is discharged, and fuel efficiency and efficiency are low.
  • UHC unburned hydrocarbon
  • the housing internal space partitioned by the rotor is required to maintain the seal between the outside of the rotary engine or the respective spaces.
  • a face seal, a peak seal, and a button seal are provided on surfaces where the housing and the rotor rub against each other, for example.
  • the face seal is mounted to the rotor so as to rotate together with the rotor, and the peak seal and the button seal are fixed to a housing that forms a friction surface with the rotor.
  • the button seal of Patent Document 1 has a problem that it is difficult to completely seal the leakage space between the face seal and the peak seal. Therefore, there is a need to improve the sealing structure so as to maximize the sealing effect of the mixer while minimizing the increase in friction loss.
  • An object of the present invention is to provide a rotary engine having a corner seal configured to seal between a rolling seal and a lobe seal in response to a gap change formed during rotation of the rotor.
  • the rotary engine of the present invention having a plurality of lobe receiving portion therein; A rotor having a lobe eccentrically rotated from a center of the housing and continuously received in the lobe receiving portion; A housing cover coupled to the housing by overlapping the lobe receptacle; And a sealing unit sealing each of the lobe accommodation parts, wherein the sealing unit includes: a rolling seal protruding from the rotor to slide with the housing cover; A lobe seal protruding from the housing to isolate the lobe receptacle adjacent to each other; And a corner seal protruding from each of the lobe seals between the housing cover and the rotor to elastically support the rolling seal.
  • the corner seal is coupled to the lobe seal so that the rolling seal is elastically supported. Accordingly, the gap between the rolling seal and the lobe seal, which varies according to the movement of the rotor, can be accurately sealed. Unlike conventional corner seals fixed on the housing lid side and unable to cope with changes in position and size of the gap, the lobe receptacle can be continuously sealed. By ensuring sealing, the thermal efficiency of the rotary engine can be further improved.
  • the corner seal of the present invention includes a body portion and a protrusion, and the lobe seal may receive a force for pressing the rotor by a locking jaw between the body portion and the protrusion. Therefore, the corner seal can be interlocked together by the lobe seal elastic member, so that the sealing unit of the present invention can be concisely implemented.
  • the corner seal has an elastic support and may be seated to be movable in the mounting groove in the thickness direction of the rotor.
  • Such a corner seal of the present invention can perform the sealing function in response to the gap is varied in the thickness direction of the rotor.
  • FIG. 1 is a longitudinal sectional view of a rotary engine according to an embodiment of the present invention.
  • FIG. 2 is an exploded perspective view of some components of the rotary engine shown in FIG. 1.
  • FIG. 2 is an exploded perspective view of some components of the rotary engine shown in FIG. 1.
  • FIG. 3 is a conceptual view showing the internal structure of the rotary engine shown in FIG.
  • FIG. 4A and 4B are perspective views of the rotor shown in FIG. 1 viewed from different directions.
  • FIG. 5 is a conceptual diagram showing an intake process inside the rotary engine shown in FIG.
  • FIG. 6 is a conceptual diagram showing a compression process inside the rotary engine shown in FIG.
  • FIG. 7 is a conceptual diagram showing an explosion process inside the rotary engine shown in FIG.
  • FIG. 8 is a conceptual view illustrating an exhaust process inside the rotary engine shown in FIG.
  • FIG. 9 is an enlarged view of the area A shown in FIG. 1.
  • FIG. 9 is an enlarged view of the area A shown in FIG. 1.
  • FIG. 10 is a perspective view of the corner seal shown in FIG. 9.
  • FIG. 11 is a conceptual view illustrating a lubrication unit included in the rotary engine illustrated in FIG. 1.
  • FIG. 1 is a longitudinal sectional view of a rotary engine according to the present invention
  • Figure 2 is an exploded perspective view of some components of the rotary engine shown in FIG. 3 is a conceptual view illustrating an internal structure of the rotary engine illustrated in FIG. 1
  • FIGS. 4A and 4B are perspective views of the rotor illustrated in FIG. 1 viewed from different directions.
  • the volume of the N operating chambers formed between the housing 110 and the rotor 120 changes as the rotor 120 eccentrically rotates inside the housing 110.
  • the four strokes of intake ⁇ compression ⁇ explosion ⁇ exhaust occur continuously.
  • the crank shaft 180 is rotated in response to the eccentric rotation of the rotor 120, and is connected to the other engine to transmit the generated power.
  • the rotary engine 100 of the present invention includes a housing 110, a spark plug 130, a rotor 120, housing covers 141 and 142, a rotor gear 170, and a crank shaft. And 180.
  • the housing 110 includes N lobe accommodation portions 111 (N is a natural number of 3 or more) therein.
  • N is a natural number of 3 or more
  • the shape of the lobe receptacle 111 and the lobes 120 'and 120 ", which will be described later, is that when there is a cloud source moving while rotating over an arbitrary shape, any point existing on the cloud source is dependent on the rotation of the cloud source. It can be designed based on the trajectory Epitrochoid curve drawn along.
  • N combustion chambers 112 communicating with the lobe receiver 111 are provided at an upper center of each lobe receiver 111.
  • the combustion chamber 112 has a recessed shape in the inner wall of the housing 110 forming the lobe accommodating portion 111.
  • the size of the combustion chamber 112 may be designed differently according to the compression ratio of the rotary engine 100.
  • the housing 110 may be provided with a spark plug 130 for discharging a flame in each combustion chamber 112 to ignite a mixer filled in the combustion chamber 112.
  • the spark plug 130 may be mounted in the mounting hole 113 of the housing 110 and disposed to be exposed to the upper portion of the combustion chamber 112.
  • the mounting hole 113 is configured to communicate with the combustion chamber 112.
  • the rotor 120 is inserted into the lobe receiving portion 111, it is configured to eccentrically rotate relative to the center of the lobe receiving portion (111).
  • the rotor 120 has N-1 lobes 120 'and 120 "that are continuously received in each lobe receiving portion 111 during eccentric rotation.
  • a support part 121 in which the rotor gear 170 is mounted is formed at the center of the rotor 120, and the crank shaft 180 inserted into the rotor gear 170 is provided in the support part 121.
  • This through hole 122 is formed.
  • the flange portion 171 of the rotor gear 170 is supported on the front surface of the support portion 121 and maintains a firm coupling state with the flange portion 171 by a fastening means such as a fastening member.
  • the front part of the rotor 120 is formed with a first storage part 123a for temporary storage of the mixer sucked through the intake side cover 141 which is one of the housing covers.
  • the first storage portion 123a has a recessed shape from the front portion of the rotor 120 toward the rear portion (ie, in the axial direction of the crank shaft 180).
  • a portion of the rotor 120 (as shown, a portion of the first storage unit 123a that does not share sidewalls with the second storage unit 123b) is bordered. May be left thin and stiffness may be reduced.
  • ribs 125 for rigidly reinforcing the rotor 120 may be protruded from a plurality of locations on the inner surface of the rotor 120 forming the first storage part 123a.
  • the at least one rib 125 ′ may be configured to be connected to the support part 121, and a height lower than the thickness of the rotor 120 so that the mixer temporarily stored in the first storage part 123a may move to the opposite side. It may be formed to include a portion having.
  • An intake port 124a communicating with the first storage part 123a is formed at the side portion of the rotor 120 to allow the sucked mixer to be introduced into the lobe accommodation part 111.
  • the intake port 124a is formed at a position where the mixer 120 can inhale while the rotor 120 rotates 90 ° to 120 ° in the counterclockwise direction.
  • a second storage unit 123b for temporarily storing the exhaust gas generated after combustion is formed.
  • the second storage portion 123b is recessed from the rear portion of the rotor 120 toward the front portion (ie, in the axial direction of the crank shaft 180).
  • Exhaust gas temporarily stored in the second storage unit 123b is discharged to the outside through the exhaust side cover 142, which is one of the housing covers.
  • An exhaust port 124b communicating with the second storage part 123b is formed at the side portion of the rotor 120 so that exhaust gas generated after combustion may flow into the second storage part 123b.
  • the exhaust port 124b is formed at a position where the rotor 120 can be evacuated after the rotor 120 is rotated 270 ° in the counterclockwise direction so that it can be disposed after more expansion than the intake amount. Such overexpansion may increase the efficiency of the rotary engine 100.
  • An intake side cover 141 is provided on the front portion of the housing 110, and an exhaust side cover 142 is provided on the rear portion of the housing 110.
  • the intake side cover 141 is coupled to the housing 110 to cover one side of the lobe receiving portion 111.
  • the intake side cover 141 is provided with a sealing part (not shown) for maintaining airtightness with the housing 110 and the rotor 120.
  • the intake side cover 141 serves as a passage for delivering the inhaled mixer to the rotor 120 while closing the housing 110. To this end, the intake side cover 141 is provided with an intake hole 141a in communication with the first storage portion 123a provided in the front portion of the rotor 120.
  • the guide gear 160 is mounted inside the intake side cover 141 facing the lobe accommodating part 111.
  • Guide gear 160 is formed in the form of a toothed ring formed along the inner circumference, and the rotor gear 170 is configured to rotate inscribed therein, thereby causing the eccentric rotation of the rotor 120 with respect to the center of the lobe receiving portion 111 Is made to guide.
  • the number of teeth of the guide gear 160 is designed in consideration of the rotation ratio of the crank shaft 180 which transmits power with the rotor 120.
  • the rotor 120 is mounted to the rotor 120.
  • a tooth is formed along the outer circumference of the rotor gear 170, and the rotor gear 170 is configured to rotate inwardly with the guide gear 160 fixed to the intake side housing cover 141.
  • the number of teeth of the rotor gear 170 is designed in consideration of the rotation ratio of the rotor 120 and the crankshaft 180.
  • a central portion of the rotor gear 170 is formed with a receiving portion 174 into which the eccentric portion 182 of the crank shaft 180 is inserted, and the eccentric portion 182 is configured to be rotatable within the receiving portion 174.
  • the eccentric portion 182 accommodated in the accommodating portion 174 rotates in response to the eccentric rotation of the rotor 120.
  • the shaft portion 181 of the crank shaft 180 is rotated N-1 revolutions in the clockwise direction.
  • the rotor gear 170 is a flat flange portion 171 configured to be supported and fixed to the support portion 121 of the rotor 120, formed on one surface of the flange portion 171 to guide gear ( Gear portion 172 configured to be inscribed in 160, the flange portion 171 is inserted into the through hole 122 of the rotor 120 when the flange portion 171 is mounted to the support portion 121 of the rotor 120, the flange portion 171 Receiving portion formed through the gear portion 172 and the boss portion 173 so that the boss portion (173) protruding from the other surface of the) and the eccentric portion (182) of the crank shaft 180 can be inserted 174 can be configured.
  • the crank shaft 180 is an axial portion 181 configured to penetrate the rotary engine 100, and an eccentric portion 182 formed eccentrically from the shaft portion 181 and inserted into the receiving portion 174 of the rotor gear 170. It includes. In the present embodiment, the shaft portion 181 may pass through the intake side cover 141 to the front and the exhaust side cover 142 to the rear. The shaft portion 181 is connected to another engine (system) and is configured to transmit power generated by the rotary engine 100 of the present invention to the other engine (system).
  • the exhaust side cover 142 is coupled to the housing 110 to cover the other side of the lobe receiving portion 111.
  • the exhaust side cover 142 seals the housing 110 and serves as a passage for discharging the generated exhaust gas.
  • the exhaust side cover 142 is provided with an exhaust hole 142a communicating with the second storage portion 123b provided at the rear portion of the rotor 120.
  • the rotary engine 100 of the present invention having the structure described above operates in four strokes of intake-compression-explosion-expansion during one cycle.
  • the movement of the rotor 120 in the housing 110 during each stroke will be described.
  • FIG. 5 to 8 are conceptual views illustrating the intake air ⁇ compression ⁇ explosion ⁇ exhaust process of the inside of the rotary engine 100 shown in FIG. 3 based on the rotation angle of the rotor 120.
  • the intake port 124a and the exhaust port 124b are provided at the side portions of the rotor 120, respectively.
  • the intake process is performed by the rotor 120 rotating in the counterclockwise direction inside the housing 110, and the rotation angle of the rotor 120 is 120 at 0 degrees. Is made while changing to degrees.
  • an intake port 124a is provided in the lobe accommodating portion 111 provided in the upper portion of the housing 110 and the combustion chamber 112 communicating therewith. Through the mixer is introduced.
  • the rotary engine 100 of the present invention is designed to allow intake to 120 degrees. This is to ensure that the efficiency of the rotary engine 100 is improved by the over-expansion in the subsequent expansion process.
  • the mixer after the intake process begins to be compressed by the rotation of the rotor 120.
  • the compression process is performed while the rotation angle of the rotor 120 varies from 120 degrees to 180 degrees.
  • the compression ratio is maximum when the rotor 120 is rotated 180 degrees, at which time the mixer is ideally completely filled in the combustion chamber 112.
  • combustion process of the mixer begins.
  • the combustion process continues to the beginning of the explosion process.
  • the combustion process starts when the rotational angle of the rotor 120 is around 160 degrees and ends completely when the rotational angle of the rotor 120 is around 200 degrees.
  • the explosion (expansion) process is performed while the rotation angle of the rotor 120 varies from 180 degrees to 270 degrees.
  • the combustion process which begins at the end of the previous compression process, is completely terminated at the beginning of the explosion process.
  • the intake process of the preceding intake is a state in which the rotation angle of the rotor 120 is 120 degrees, that is, the intake of the mixer by the corresponding volume when the rotor 120 is rotated 240 degrees in this figure, while the expansion process Is the rotation angle of the rotor 120 forming a larger volume than this is up to 270 degrees. Therefore, the rotary engine 100 of the present invention can obtain an overexpansion effect of achieving expansion larger than the intake volume.
  • the exhausting process is performed while the rotation angle of the rotor 120 varies from 270 degrees to 360 degrees.
  • the generated exhaust gas is discharged through the exhaust port 124b while the rotor 120 rotates counterclockwise from 270 to 360 degrees.
  • FIG. 9 is an enlarged view of the area A shown in FIG. 1, and FIG. 10 is a perspective view of the corner seal 147 shown in FIG. 9. 1, 9 and 10, the rotary engine 100 according to an embodiment of the present invention includes a sealing unit 107.
  • the sealing unit 107 may function to respectively seal the space of the lobe accommodating part 111 where the volume is changed between the rotor 120 and the housing 110 to compress and expand the mixer.
  • the sealing unit 107 includes a rolling seal 127, a lobe seal 117, and a corner seal 147.
  • the rolling seals 127 are formed on the front and rear surfaces in the thickness direction of the rotor 120 (the axial direction in which the crank shaft 180 extends), respectively, and the intake side cover 141 and the exhaust side cover 142 and It is formed to protrude so as to slide.
  • the rolling seal 127 may be formed to extend along the circumference of the N-1 lobes formed in the rotor 120 to form a loop (loop). .
  • the rolling seal 127 When the rotor 120 rotates, the rolling seal 127 may be configured to maintain a close contact with the housing covers 141 and 142. Specifically, the side groove 127a may be formed to be recessed on the surface of the rotor 120, and the rolling seal 127 may be seated in the side groove 127a. In this case, the side elastic member 127b supported by the rolling seal 127 and the side groove 127a may be interposed.
  • the rolling seal 127 forms a loop to maintain close contact with the housing lids 141 and 142, thereby preventing the mixer from leaking into the gap between the rotor 120 and the housing lids 141 and 142. .
  • the rolling seal 127 in close contact with the intake side cover 141 restricts the mixer in the lobe accommodating part 111 from leaking to the intake hole 141a and the first storage part 123a. can do.
  • the rolling seal 127 in close contact with the exhaust side cover 142 may limit the flow of the mixer in the lobe accommodating part 111 toward the second storage part 123b and the exhaust hole 142a.
  • the lobe seal 117 serves to isolate the N lobe accommodation portions 111 in which mixers having different compression or expansion states are accommodated.
  • N peak portions 114 may be formed in the housing 110 having the N lobe accommodation portions 111, as shown in FIG. 3.
  • the lobe seal 117 may be formed to protrude from each of the N peak portions 114 to slide on the outer surface of the rotor 120 (the surface facing the housing 110 in the radial direction of the crank shaft 180). .
  • the lobe seal 117 may be accommodated in the apex groove 117a, and the lobe seal 117 may be supported by the apex groove 117a by the apex elastic member 117b.
  • the lobe seal 117 may protrude from the housing 110 to elastically support and adhere to the rotor 120.
  • the lobe seal 117 may be provided as many as the lobe accommodation portion 111.
  • the corner seal 147 functions to seal the space between the rolling seal 127 and the lobe seal 117.
  • the rolling seal 127 since the rolling seal 127 is formed to be inserted into the side groove 127a, the rolling seal 127 is positioned at a point spaced inward from the outer surface of the rotor 120. Therefore, the lobe seal 117 and the rolling seal 127 sliding on the outer surface of the rotor 120 may form a space spaced from each other. Through this space, the spaces of the lobe accommodation portions 111 may communicate with each other.
  • the space between the rolling seal 127 and the lobe seal 117 may vary in position and size. This may be due to the fact that the angle formed by the outer surface of the rotor 120 with respect to the peak portion 114 is continuously changed. As described above, since the outer surface of the rotor 120 is elastically supported with the lobe seal 117, leakage through the outer surface of the rotor 120 may be prevented, but the rolling seal 127 and the lobe seal 117 may be prevented. Moving spaces between them are difficult to seal accurately.
  • the corner seal 147 provided in the rotary engine 100 of the present embodiment protrudes between the housing covers 141 and 142 and the rotor 120 from each lobe seal 117 to be elastically supported by the rolling seal 127. It is made of a shape. As shown in FIGS. 1 and 9, the corner seal 147 may extend to be inserted into a space spaced between the housing covers 141, 142 and the rotor 120 at both ends of the lobe seal 117. An end of the extended corner seal 147 may be made to slide in contact with the rolling seal 127. Since the corner seal 147 extends from the lobe seal 117, the corner seal 147 also has a radius of the crank shaft 180 as the lobe seal 117 moves in the radial direction of the crank shaft 180. Can be moved in a direction.
  • corner seal 147 of the present embodiment is made to move in conjunction with the lobe seal 117, the corner seal 147 may more effectively seal the space between the rolling seal 127 and the lobe seal 117.
  • corner seal 147 is fixed to the housing cover (141, 142) side could not cope with the position and size change of the gap, each lobe receiving portion 111 can be continuously sealed, rotary engine There is an effect that the thermal efficiency of (100) can be improved.
  • the corner seal 147 of the present embodiment may include a body portion 147a and a protrusion 147b.
  • the body portion 147a is a portion formed to achieve engagement with the lobe seal 117 and may be formed in a cylindrical shape extending in the thickness direction in which the lobe seal 117 extends.
  • the body portion 147a may include a receiving groove 147c formed to receive an end portion of the sealing rod of the lobe seal 117.
  • the body portion 147a may be inserted into both ends of the lobe seal 117 in the axial direction of the crank shaft 180.
  • the protrusion 147b is protruded to contact the rolling seal 127 at the body 147a. When the rotor 120 rotates, the protrusion 147b may slide on the rolling seal 127 and the rotor 120.
  • the protrusion 147b is formed to a size sufficient to seal the space in consideration of the distance between the rolling seal 127 and the lobe seal 117 and the distance between the rotor 120 and the housing covers 141 and 142. Can be.
  • the protrusion 147b and the receiving groove 147c may be formed to protrude and recess in the same direction from each other on the outer circumferential surface of the body 147a. Accordingly, the lobe seal 117 and the protrusion 147b may slide on the outer surface of the rotor 120 and a surface adjacent thereto, respectively.
  • the locking jaw 147d may be formed by the protrusion 147b and the receiving groove 147c so that the corner seal 147 receives the force that the lobe seal 117 presses the outer surface of the rotor 120. have.
  • the protruding portion 147b may include a locking step 147d configured to contact the lobe seal 117 inserted into the receiving groove 147c. That is, the locking jaw 147d may be formed by overlapping the protrusion 147b and the receiving groove 147c with each other.
  • the protrusion 147b (the entire corner seal 147) is also moved toward the rolling seal 127 by the locking jaw 147d, It can also be elastically supported.
  • the corner seal 147 and the lobe seal 117 may be coupled to move relative to each other in the axial direction of the crank shaft 180.
  • the lobe seal 117 may be inserted into the receiving groove 147c so as to be slidable in the surface forming the locking step 147d.
  • the corner seal 147 of the present embodiment includes a body portion 147a and a protrusion 147b, and has a lobe seal by a locking step 147d between the body portion 147a and the protrusion 147b.
  • 117 may receive an elastic force for pressing the rotor 120.
  • the corner seal 147 which is interlocked with the lobe seal 117 to form the pressing force may be implemented by a simple structure.
  • the corner seal 147 may include an elastic support part 147e.
  • the elastic support 147e may generate an elastic force in the axial direction of the crank shaft 180 when the corner seal 147 is mounted to the lobe seal 117.
  • the elastic support part 147e may be configured to connect the body part 147a of the corner seal 147 and the housing 110 with each other.
  • the elastic support 147e When the elastic support 147e is mounted on the housing 110 supporting the lobe seal 117 as shown in the illustrated position, the elastic support 147e may be configured to generate a compressive force. That is, the elastic support part 147e may be formed to have a force for pulling the corner seal 147 in the direction from the housing covers 141 and 142 toward the rotor 120 in the axial direction of the crank shaft 180.
  • the mounting cover 143 may be formed in the housing covers 141 and 142 of the present embodiment to accommodate a part of the corner seal 147.
  • the mounting groove 143 may be formed in the housing covers 141 and 142 so as to be recessed in a surface facing the housing 110 or the rotor 120.
  • the mounting groove 143 may be formed in a shape for receiving a portion of the cylindrical body portion 147a and the protrusion 147b protruding from the body portion 147a.
  • the mounting groove 143 may have a larger space than the corner seal 147 so that the corner seal 147 seated therein is movable.
  • the direction in which the corner seal 147 can move is the direction toward the rolling seal 127 (the radial direction of the crankshaft 180), and the direction toward the lobe seal 117 (the thickness direction of the rotor 120). Can be.
  • an elastic support part 147f for supporting and pressing the corner seal 147 may be mounted in the mounting groove 143.
  • the elastic support part 147f fixed in the mounting groove 143 is configured to generate a tensile force to press the corner seal 147 in the direction toward the rotor 120 unlike the elastic support part 147e mounted to the housing 110. Can be.
  • the corner seal 147 is provided with an elastic support portion 147e and is seated to be movable in the mounting groove 143, so that the corner seal 147 of the present embodiment is disposed in the thickness direction of the rotor 120 and the housing 120.
  • the sealing function may be performed in response to the gap between the covers 141 and 142 being variable. Accordingly, the corner seal 147 is interlocked with the lobe seal 117 to move in the radial direction (up and down direction in FIG. 9) of the rotor 120, and between the rolling seal 127 and the lobe seal 117. The gap can be effectively sealed.
  • FIG. 11 is a longitudinal sectional view showing a lubrication unit included in the rotary engine 100 shown in FIG. 1.
  • the rotary engine 100 of the present invention may further include a lubrication unit 190.
  • the lubrication unit 190 includes an oil pan 191, an oil pump 192, and an oil supply flow path 193. These components each serve to store oil, pump oil, and supply oil to the corner seal 147.
  • the oil storage cover 150 may be coupled to the intake side cover 141.
  • an intake hole 141a may be formed at a rear surface of the intake side cover 141 that is coupled to face the rotor 120, and an oil pump 192 may be mounted at a front surface opposite to the rotor 120.
  • the oil storage cover 150 may be formed to cover the front surface of the intake side cover 141 to accommodate the oil pump 192.
  • an oil pan 191 may be formed in communication with a space formed by the oil storage cover 150 and the intake side cover 141 to fill the oil.
  • the oil pan 191 and the oil pump 192 may be connected to each other by a pipe or a tube for pumping oil, and an oil strainer 191a for filtering oil may be immersed in the oil pan 191 at the end of the pipe or the tube. It may be further provided to be.
  • the oil pump 192 may be, for example, a trochoid pump that sucks oil by eccentric rotation of the rotating body. In particular, it may be spaced apart to rotate in parallel with the crank shaft 180 as shown in FIG.
  • the chain gear 183 may be mounted on the outer circumferential surface of the crank shaft 180, and the trocoid pump and the crank shaft 180 may be connected to each other by the chain member 192a. Therefore, the rotational force generated on the crankshaft 180 in accordance with the operation of the rotary engine 100 according to the present invention can be transmitted to the trocoid pump.
  • the oil supply passage 193 may be connected to supply the oil pumped up to the oil pump 192 to the corner seal 147. That is, one end is connected to the discharge side of the oil pump 192 and the other end is located at a point adjacent to the corner seal 147.
  • the operation of the oil pump 192 is started as power is generated in the crankshaft 180, and the oil filled in the oil pan 191 is cornered through the oil supply flow passage 193. It is operated to be supplied to the seal 147.
  • lubrication is performed on the friction surface of the corner seal 147, and oil is also supplied to the rolling seal 127 and the lobe seal 117 through the friction surface of the corner seal 147. Lubrication can be performed.
  • the oil pump 192 may be operated in conjunction with the crank shaft 180 by the chain member 192a. In this way, the oil pump 192 can be operated without the need for additional driving means. Furthermore, as the output of the engine is increased, the oil supply may be increased so that a variable lubrication action corresponding to the output of the engine may be realized.
  • the oil supply passage 193 provided in the present invention may include a housing passage 193a and a supply tube 193b.
  • the housing flow passage 193a is an inner flow passage passing through the housing covers 141 and 142
  • the supply tube 193b has a form of an outer flow passage formed outside the housing 110 and the housing covers 141 and 142.
  • the housing flow passage 193a may be positioned such that one end thereof is exposed to the outer surface of the housing cover 141 and the other end thereof is adjacent to the corner seal 147. As shown in FIG. 9, the housing flow passage 193a may be formed to straightly penetrate the intake side cover 141 in the radial direction of the crankshaft 180.
  • the supply tube 193b may be formed outside the housing 110 and the housing covers 141 and 142 so as to communicate the oil pump 192 and the housing flow passage 193a with each other. That is, one end may be connected to the discharge side end of the oil pump 192, and the other end may be connected to each other where the housing flow path 193a is exposed to the outer surfaces of the housing covers 141 and 142.
  • the oil supply passage 193 is formed of a combination of the housing passage 193a and the supply tube 193b, the oil supply by the separate passage may be performed without using the flow of the mixer.
  • the present invention may be used and applied in the industrial field using a rotary engine that produces power by rotational motion.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

La présente invention concerne un moteur rotatif comprenant : un carter comportant une pluralité de parties de réception de lobes, disposées en son sein ; un rotor, entraîné en rotation tout en étant disposé de manière excentrique par rapport au centre du carter, et comportant des lobes reçus successivement dans les parties de réception de lobes ; un couvercle de carter, accouplé au carter tout en chevauchant les parties de réception de lobes ; et une unité d'étanchéité permettant de sceller chacune des parties de réception de lobes, l'unité d'étanchéité comprenant : des joints d'étanchéité de roulement faisant saillie à partir du rotor, de façon à coulisser sur le couvercle de carter ; des joints d'étanchéité de lobes, faisant saillie à partir du carter, de façon à séparer les parties de réception de lobes adjacentes les unes des autres ; et des joints d'étanchéité d'angle faisant saillie à partir de chacun des joints d'étanchéité de lobes, s'étendant entre le couvercle de carter et le rotor, et soutenus élastiquement sur les joints d'étanchéité de roulement. Par conséquent, l'espace variable entre chaque joint d'étanchéité de lobes et chaque joint d'étanchéité de roulement peut être efficacement scellé.
PCT/KR2018/003886 2017-04-27 2018-04-03 Moteur rotatif WO2018199490A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201880027416.9A CN110546360B (zh) 2017-04-27 2018-04-03 转子发动机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2017-0054633 2017-04-27
KR1020170054633A KR20180120526A (ko) 2017-04-27 2017-04-27 로터리 엔진

Publications (1)

Publication Number Publication Date
WO2018199490A1 true WO2018199490A1 (fr) 2018-11-01

Family

ID=63919846

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2018/003886 WO2018199490A1 (fr) 2017-04-27 2018-04-03 Moteur rotatif

Country Status (3)

Country Link
KR (2) KR20180120526A (fr)
CN (1) CN110546360B (fr)
WO (1) WO2018199490A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113818960B (zh) * 2021-10-12 2022-07-01 陕西新年动力科技集团有限公司 一种转子发动机
KR20230165635A (ko) 2022-05-27 2023-12-05 숭실대학교산학협력단 내부 스프링 방식 반켈 로터 및 이를 구비한 반켈 시스템

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3872838A (en) * 1970-11-30 1975-03-25 Volkswagenwerk Ag Combustion engine having a rotary type piston arrangement
KR20140022029A (ko) * 2011-03-29 2014-02-21 리퀴드피스톤 인크. 사이클로이드 로터 엔진
JP2016109061A (ja) * 2014-12-08 2016-06-20 マツダ株式会社 ロータリーピストンエンジンのアペックスシール構造
WO2016145247A1 (fr) * 2015-03-10 2016-09-15 Liquidpiston, Inc. Moteur rotatif épitrochoïde à rendement et densité de puissance élevés
JP2016211522A (ja) * 2015-05-13 2016-12-15 行廣 睦夫 バンケル型ロータリーエンジンの点火方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4923607U (fr) * 1972-06-07 1974-02-28
US3930767A (en) * 1974-07-16 1976-01-06 General Motors Corporation Circular rotor side seal for rotary machines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3872838A (en) * 1970-11-30 1975-03-25 Volkswagenwerk Ag Combustion engine having a rotary type piston arrangement
KR20140022029A (ko) * 2011-03-29 2014-02-21 리퀴드피스톤 인크. 사이클로이드 로터 엔진
JP2016109061A (ja) * 2014-12-08 2016-06-20 マツダ株式会社 ロータリーピストンエンジンのアペックスシール構造
WO2016145247A1 (fr) * 2015-03-10 2016-09-15 Liquidpiston, Inc. Moteur rotatif épitrochoïde à rendement et densité de puissance élevés
JP2016211522A (ja) * 2015-05-13 2016-12-15 行廣 睦夫 バンケル型ロータリーエンジンの点火方法

Also Published As

Publication number Publication date
CN110546360A (zh) 2019-12-06
CN110546360B (zh) 2022-05-17
KR20210103994A (ko) 2021-08-24
KR20180120526A (ko) 2018-11-06
KR102329615B1 (ko) 2021-11-22

Similar Documents

Publication Publication Date Title
US7614382B2 (en) Aspiration plate for planetary rotary internal combustion engine
US5277158A (en) Multiple vane rotary internal combustion engine
KR890000571B1 (ko) 로우타리 엔진
WO2012079468A1 (fr) Moteur rotatif et son unité de rotor
WO2018199490A1 (fr) Moteur rotatif
US3314401A (en) Two-stroke cycle rotary engine
US3968776A (en) Rotary crankless machine
KR20190130934A (ko) 로터리 엔진
WO2012044051A2 (fr) Moteur rotatif et moteur rotatif multi-étagé utilisant celui-ci
WO2018216894A1 (fr) Moteur rotatif
US4617886A (en) Rotary engine
RU2078221C1 (ru) Русский ротор веселовского "ррв"
US7100566B2 (en) Operating method for a rotary engine and a rotary internal combustion engine
US20150300173A1 (en) Ignition engine of the rotary type with a double rotation center
US3973526A (en) Rotary combustion engine
WO2014010792A1 (fr) Structure de moteur à combustion interne rotatif
US3996898A (en) Rotary combustion engine apex seal arrangement
KR101972907B1 (ko) 흡배기포트 구조를 개선한 로터리 엔진
RU2271456C2 (ru) Роторный двигатель внутреннего сгорания
KR101919712B1 (ko) 크랭크축 및 이를 포함하는 로터리 엔진
KR101980014B1 (ko) 흡배기 구조를 개선한 다기통 로터리 엔진
US3176665A (en) Rotary piston internal combustion engine
KR20190124057A (ko) 로터 일체형 사이드씰을 구비하는 로터리 엔진
KR20180120524A (ko) 로터리 엔진
US20220381145A1 (en) Modular rotary engine

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18790616

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18790616

Country of ref document: EP

Kind code of ref document: A1